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WO2018121884A1 - Courroie d'entraînement pour une transmission à variation continue avec des segments transversaux et un empilement annulaire - Google Patents

Courroie d'entraînement pour une transmission à variation continue avec des segments transversaux et un empilement annulaire Download PDF

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Publication number
WO2018121884A1
WO2018121884A1 PCT/EP2017/025371 EP2017025371W WO2018121884A1 WO 2018121884 A1 WO2018121884 A1 WO 2018121884A1 EP 2017025371 W EP2017025371 W EP 2017025371W WO 2018121884 A1 WO2018121884 A1 WO 2018121884A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive belt
transverse
transverse segment
projection
hole
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2017/025371
Other languages
English (en)
Inventor
Cornelis Johannes Van Der Meer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to KR1020197021873A priority Critical patent/KR20190104553A/ko
Priority to CN201780080545.XA priority patent/CN110114591B/zh
Priority to JP2019555059A priority patent/JP7009502B2/ja
Publication of WO2018121884A1 publication Critical patent/WO2018121884A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G5/00—V-belts, i.e. belts of tapered cross-section
    • F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
    • F16G1/00—Driving-belts
    • F16G1/22—Driving-belts consisting of several parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts

Definitions

  • This disclosure relates to a drive belt for a continuously variable transmission with two pulleys and the drive belt.
  • a drive belt is known from the international patent application publication WO2015/063132-A1 and comprises a row of transverse segments mounted on a stack of several, mutually nested continuous bands, i.e. flat and thin rings, each.
  • the transverse segments define a slot for accommodating and confining a respective circumference section of the ring stack, while allowing the transverse segments to move along the circumference of the ring stacks.
  • This particular type of drive belt is also referred to as a push-type drive belt or pushbelt.
  • the axial, radial and circumference directions are defined relative to the drive belt when placed in a circular posture. Furthermore, a thickness dimension of the transverse segments is defined in the circumference direction of the drive belt, a height dimension of the transverse segment is defined in the said radial direction and a width dimension of the transverse segment is defined in the said axial direction.
  • the known transverse segments each comprise a base portion, a middle portion and a top portion.
  • the middle portion of the transverse segments extends in radial direction interconnecting the said base and top portions thereof.
  • the transverse segments define a slot between the base portion and the top portion thereof for accommodating a respective ring stack of the drive belt.
  • a radially outward facing bottom surface thereof contacts and supports the ring stack in radial outward direction.
  • At least a part of a front main body surface of the transverse segment abuts against at least a part of the back main body surface of a respectively preceding transverse segment in the said row, whereas at least a part of the back main body surface of the transverse segment abuts against at least a part of the front main body surface of a respectively succeeding transverse segment.
  • At least one of these front and back main body surfaces of the transverse segment for example the front main body surface includes an axially extending, convexly curved surface part. This curved surface part divides the front main body surface into a radially outer and a radially inner surface parts that are oriented at an angle relative to one other.
  • Abutting transverse segments in the drive belt are able to tilt relative to one another, while remaining in mutual contact at and through such curved surface part that is therefore denoted tilting edge hereinafter.
  • the tilting edge allows the row of the transverse segments of the drive belt to follow a local curving of the ring stacks imposed by the transmission pulleys.
  • the transverse segment is further provided with a projection that protrudes from its front main body surface and with a corresponding hole that is provided in its back main body surface.
  • the projection of the said succeeding transverse segment is at least partially located in the hole of the said preceding transverse segment, such that a mutual displacement of the abutting transverse segments in a plane perpendicular to the circumference direction of the drive belt is prevented or, at least, limited.
  • the projection and the hole are of a similar overall shape, e.g. predominantly cylindrical or slightly conical.
  • the transverse segments can move relative to the ring stacks along the circumference thereof.
  • This has the advantage that during operation of the drive belt the ring stack is tensioned to a relatively low level in relation to a torque transmitted by the drive belt between the pulleys, at least compared to other types of drive belt.
  • a sliding movement or slip between the transverse segments and the ring stack is known to bring about a small, but notional friction loss. It is known that such sliding movement can be favourably minimised by arranging the tilting edge of the transverse segments as close to the radial inside of the ring stack as possible in the height direction. In theory, in this respect, the tilting edge is preferably arranged to coincide with the carrying surfaces of the transverse segment in question.
  • locating the tilting edge close to the carrying surface brings about a problem or disadvantage that may be understood as follows.
  • the closer the tilting edge is to the carrying surface the sharper a transition edge there between must be.
  • a sharper transition edge results in a higher contact stress in the ring stack.
  • such disadvantage can, surprisingly, be mitigated by including an offset in vertical direction between the projection and the hole of the individual transverse segment, in particular by locating the hole somewhat lower, i.e. more towards the radial inside of the drive belt, than the projection.
  • the transverse segments will be tilted forward in the row of the drive belt, because of the forced insertion of the projection into the (lower lying) hole.
  • a contact between the radial inside of the ring stack and the transition edge between the carrying surface and the tilting edge is favourably avoided or, at least, reduced in its intensity .
  • the tilting edge is separated from the carrying surfaces by around 1 mm, such that a radius of curvature of the transition edge can be 0.5 mm or more.
  • the offset 0 in radial inward direction of the hole relative to the projection of the individual transverse segment in accordance with the present disclosure can be quantified geometrically as follows:
  • 0_min Rr_min - (Rr_min A 2 - 3 ⁇ 4 « D A 2) (1), with 0_min representing a minimal value for the said offset 0, with Rr_min representing a minimum radius of longitudinal curvature of the drive belt, in particular at the transmission pulleys, and with D representing the thickness of the transverse segment.
  • the transverse segments in the drive belt are tilted forward in the drive belt to such an extent that the transition edge lies to the radial inside of a virtual circle of radius Rr_min and intersecting an edge between the carrying surface and the back main body surface .
  • a minim offset 0_min of 11 micrometre is calculated with equation (1) .
  • a practical design value for the said offset 0 that allows for production spread and other uncertainties some is then 1.5 up to 5 times 0_min or between 15 and 75 micron.
  • such actually applied offset 0 and thus the said forward tilting of the transverse segment imposed thereby is limited to five times, more preferably to three times such minimally required value 0_min. Otherwise, the alignment forces between the projection become unnecessarily high and/or the ring stack is forced to contact a back edge of the carrying surface instead.
  • FIG. 1 provides a schematic perspective view of a continuously variable transmission with a drive belt running over two pulleys;
  • FIG. 2 provides a schematic cross section of the known drive belt oriented in the circumference direction thereof;
  • FIG. 3 provides a schematic width-wise oriented view of a transverse segment of the known drive belt
  • figure 4 is an enlargement of a part of the known transverse segment depicted in figure 3;
  • FIG. 5 is an enlargement of a part of a novel transverse segment
  • FIG. 6 schematically illustrates a straight trajectory part of the drive belt incorporating the novel transverse segment.
  • Figure 1 schematically shows a continuously variable transmission, such as for utilization in a motor vehicle between the prime mover and the drive wheels thereof.
  • the continuously variable transmission is indicated in general by the reference sign 1.
  • the continuously variable transmission 1 comprises two pulleys 2, 3 and a drive belt 6 that is provided in a closed loop around the pulleys 2, 3.
  • the pulleys 2, 3 are each provided with a pulley shaft 4 and with two pulley sheaves 7, 8, whereof a first pulley sheave 7 is fixed to the pulley shaft 4 of the respective pulley 2, 3 and whereof a second pulley sheave 8 is axially displaceable relative to such pulley shaft 4, while being fixed thereto in rotational direction.
  • the drive belt 6 is clamped at a running radius Rr at each pulley 2, 3 by and between the respective pulley sheaves 7, 8 thereof, which running radii Rr can be varied to vary the speed ratio of the transmission by moving the pulley sheaves 7, 8 of the pulleys 2, 3 towards, respectively away from each other.
  • the drive belt 6 comprises two sets of mutually radially stacked continuous bands or rings, denoted ring stacks 9 hereinafter.
  • Transverse segments 10 of the drive belt 6 are arranged on the ring stacks 9 forming an essentially contiguous row along the entire circumference thereof. For the sake of simplicity, only a part of these transverse segments 10 are shown in figure 1.
  • the transverse segments 10 are provided movable with respect to the ring stacks 9, at least along the circumference thereof. As a result, a torque can be transmitted between the transmission pulleys 2, 3 by means of friction and by the transverse segments 10 pressing against one another and pushing each other forward along the circumference of the ring stacks 9 in a direction of rotation of the pulleys 2, 3.
  • the transverse segments 10 and the (rings of the) ring stacks 9 of the drive belt 6 are typically made of steel. This particular type of transmission 1 and its principal operation are well-known per se.
  • an exemplary embodiment of the drive belt 6 is shown in cross section oriented in length or circumference direction C thereof, i.e. perpendicular to the width or axial direction A and the height or radial direction R of the drive belt 6.
  • the transverse segment 10 of figure 2 is shown in a side elevation in the axial direction A.
  • the ring stacks 9 are shown in cross-section and one transverse segments 10 of the drive belt 6 is shown in a front elevation.
  • the ring stacks 9 are in this case composed of five individual flat, thin and flexible endless rings 5 each, which endless rings 5 are mutually concentrically stacked in the radial direction R to form the respective ring stack 9. In practice, however, these ring stacks 9 often comprise more than five endless rings 5, e.g. nine or twelve or possibly even more.
  • the transverse segment 10 are shown to successively comprise in the radial direction R a base portion 13 of predominantly trapezoidal shape, a relatively narrow middle portion 14 and a top portion 15 of predominantly triangular shape.
  • slots 33 are defined between the base portion 13 and the top portion 15, wherein the ring stacks 9 are accommodated.
  • a radially outward facing carrying surface 42 of the base portion 13 contacts the radial inside of a respective ring stack 9 during operation.
  • a front surface of the transverse segment 10 is indicated in general by the reference sign 11, whereas a back surface of the transverse segment 10 is indicated in general by the reference sign 12.
  • the front surface 11 and the back surface 12 are generally indicated as main body surfaces 11, 12.
  • at least a part of the front surface 11 of the transverse segment 10 abuts against at least a part of the back surface 12 of a succeeding transverse segment 10
  • at least a part of the back surface 12 of the transverse segment 10 abuts against at least a part of the front surface 11 of a preceding transverse segment 10.
  • the transverse segment 10 takes-up a clamping force exerted between the discs 7, 8 of each pulley 2, 3 via contact faces 37 thereof, one such contact face 37 being provided at each axial side of the transverse segment 10.
  • These contact faces 37 are mutually diverging in radial outward direction such that an acute angle is defined there between that is denoted the belt angle ⁇ and that closely matches a pulley angle ⁇ defined between the pulley sheaves 7, 8 of the pulleys 2, 3.
  • the transverse segment 10 is provided with a projection 40 that protrudes from its front surface 11 and with a corresponding hole 41 that is provided in its back surface 12.
  • the projection 40 of the trailing transverse segment 10 is at least partially located in the hole 41 of the leading transverse segment 10, such that mutual displacement of these adjacent transverse segments 10 in a plane perpendicular to the circumference direction C of the drive belt 3 is prevented or, at least, limited.
  • a nominal clearance of between 10 and 50 micron is provided between an outer circumference of the projection 40 and an inner circumference of the hole 41, i.e. the projection/hole-clearanee.
  • a rocking edge 18 is defined at the front surface 11 in the base portion 13 of the transverse segment 10.
  • the rocking edge 18 is represented by a convexly curved area of the front surface 11, which area separates two sections of the said front surface 11 in the radial direction R, which two sections are oriented at an angle relative to one other.
  • An important function of the rocking edge 18 is to provide the mutual pushing contact between the adjacent transverse segments 10 when these are in a slightly rotated, i.e. tilted position relative to one another at the pulleys 2, 3.
  • the rocking edge 18 preferably extends along the full local width of the transverse segments 10.
  • the rocking edge 18 is preferably located close to the carrying surfaces 42, i.e. at minimal distance Drc radial inward thereof. However, the smaller such distance Drc is, the sharper a transition edge 50 between the front surface 11 and the carrying surfaces 42 of the transverse segment 10 will be.
  • Drc minimal distance
  • This latter aspect of the design of the transverse segment 10 is illustrated in figure 4 in an enlargement of the area E of figure 3 indicted by the dotted circle.
  • a relatively large rocking edge -to-carrying surface distance Drc is illustrated, allowing the transition edge 50 to be provided with a relatively large radius of curvature Rte, at least in comparison with the design of the transverse segment 10 on the right side of figure 4 with a relatively small rocking edge - to-carrying surface distance Drc.
  • the radius of curvature Rte is somewhat smaller than the rocking edge-to-carrying surface distance Drc in order to reliably ensure in mass manufacture that the rocking edge 18 does not overlap with the transition edge 50.
  • the transition edge 50 is depicted as a circular arc of radius Rte .
  • the transition edge 50 may not be so uniformly shaped, in which case its contour is approximated by a (closest fit of a) circular arc of radius Rte, at least within the context of the present disclosure.
  • the transition edge radius Rte between the carrying surfaces 42 and the front surface 11 might seem unimportant.
  • this transition edge 50 does in practice arrive in contact with the radial inside of a respective ring stack 9 raising the overall stress level thereof. More in particular in this latter respect, a substantial stress raising effect was found to occur when the radius Rte of the transition edge 50 becomes less than 0.5 mm, in particular less than 0.3 mm.
  • such contact between the transition edge 50 and the ring stack 9 can favourably be avoided, or at least reduced in intensity by providing an offset 0 between the radial position of the projection 40 and the radial position of the hole 41 of the transverse segment 10.
  • FIG 5 This novel design of the transverse segment 10 is schematically illustrated in figure 5 in an enlargement of a part thereof, which part corresponds to area F indicated in figure 3 by the dotted oval in relation to the transverse segment 10.
  • the central axis of the cylindrical projection 40 is indicated by the solid line CA40 and the central axis of the hole 41 is indicated by the dashed line CA41.
  • the said offset 0 thus corresponds to the separation between the central axis CA40 of the cylindrical projection 40 and the central axis CA41 of the hole 41.
  • offset 0 amounts between 15 and 75 micrometre or so for the typical thickness of the transverse segment 10 of between 1.4 and 1.8 mm. So even on the scale of figure 5, the offset 0 has been exaggerated therein.
  • the transverse segments 10 are forced to tilt forward relative to the ring stacks 9 by the forced insertion of the projection 40 of a first transverse segment 10 into the (lower lying) hole 41 of an adjacent transverse segment 10 as these are pressed together in the row of the drive belt 3.
  • the contact between the radial inside of the respective ring stack 9 and the transition edge 50 of the transverse segments 10 can be favourably avoided in a straight section of the drive belt 3 crossing between the transmission pulleys 2, 3, as is schematically illustrated in figure 6.
  • the transverse segments 10 also enter between the two pulley sheaves 7, 8 in such tilted position relative to the ring stacks 9, whereby a radial position of the transition edge 50 of a respective transverse segment 10, clamped between pulley sheaves 7, 8, is somewhat smaller than a radial positon of an opposite edge of the carrying surfaces 42 on the side of the back surface 12 of the transverse segment 10.
  • the contact between the radial inside of the respective ring stack 9 and the transition edge 50 between the carrying surface and the tilting edge is at least favourably reduced in its intensity.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Pulleys (AREA)

Abstract

La présente invention concerne une courroie d'entraînement (6) pour une transmission à variation continue de type courroie et poulie comprenant une rangée de segments transversaux (10) montés sur un empilement (9) de plusieurs anneaux mutuellement emboîtés. Les segments transversaux (10) sont pourvus d'une saillie (40) qui fait saillie à partir d'une surface avant (11) de ceux-ci et d'un trou correspondant (41) qui est disposé dans une surface arrière (12) de ceux-ci. Un décalage est prévu entre la saillie (40) et le trou (41) dans la direction radiale (R) de la courroie d'entraînement (6) de sorte que, dans la rangée de segments transversaux (10) dans la courroie d'entraînement (6), ceux-ci soient inclinés vers l'avant par l'insertion forcée de la saillie (40) dans le trou (41).
PCT/EP2017/025371 2016-12-27 2017-12-27 Courroie d'entraînement pour une transmission à variation continue avec des segments transversaux et un empilement annulaire Ceased WO2018121884A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
KR1020197021873A KR20190104553A (ko) 2016-12-27 2017-12-27 횡방향 세그먼트와 링 스택을 갖는 무단 변속기용 구동 벨트
CN201780080545.XA CN110114591B (zh) 2016-12-27 2017-12-27 用于无级变速器的具有横向部件和环件套组的传动带
JP2019555059A JP7009502B2 (ja) 2016-12-27 2017-12-27 横断部材とリングスタックとを備える、無段変速機に用いられる駆動ベルト

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL1042198A NL1042198B1 (en) 2016-12-27 2016-12-27 A drive belt for a continuously variable transmission with transverse segments and a ring stack
NL1042198 2016-12-27

Publications (1)

Publication Number Publication Date
WO2018121884A1 true WO2018121884A1 (fr) 2018-07-05

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PCT/EP2017/025371 Ceased WO2018121884A1 (fr) 2016-12-27 2017-12-27 Courroie d'entraînement pour une transmission à variation continue avec des segments transversaux et un empilement annulaire

Country Status (5)

Country Link
JP (1) JP7009502B2 (fr)
KR (1) KR20190104553A (fr)
CN (1) CN110114591B (fr)
NL (1) NL1042198B1 (fr)
WO (1) WO2018121884A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112943862A (zh) * 2019-12-10 2021-06-11 罗伯特·博世有限公司 用于传动带的横向段及用于无级变速器的传动带

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000179626A (ja) * 1998-12-11 2000-06-27 Nissan Motor Co Ltd 無段変速機用ｖベルト
WO2014102225A1 (fr) * 2012-12-24 2014-07-03 Robert Bosch Gmbh Courroie d'entraînement avec anneau de support et segments transversaux
WO2015063132A1 (fr) 2013-11-01 2015-05-07 Robert Bosch Gmbh Procédé de fabrication d'un segment transversal pour courroie de poussée pour une transmission à variation continue et segment transversal ainsi obtenu

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3562645B2 (ja) 2002-02-26 2004-09-08 日産自動車株式会社 無段変速機用ベルトのエレメントおよびその製造方法
EP2716933B1 (fr) 2011-05-27 2016-07-20 Toyota Jidosha Kabushiki Kaisha Courroie d'entraînement et procédé d'assemblage pour courroie d'entraînement
CN104040216B (zh) * 2012-12-27 2015-11-25 本田技研工业株式会社 金属元件的变形状态检测装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000179626A (ja) * 1998-12-11 2000-06-27 Nissan Motor Co Ltd 無段変速機用ｖベルト
WO2014102225A1 (fr) * 2012-12-24 2014-07-03 Robert Bosch Gmbh Courroie d'entraînement avec anneau de support et segments transversaux
WO2015063132A1 (fr) 2013-11-01 2015-05-07 Robert Bosch Gmbh Procédé de fabrication d'un segment transversal pour courroie de poussée pour une transmission à variation continue et segment transversal ainsi obtenu

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112943862A (zh) * 2019-12-10 2021-06-11 罗伯特·博世有限公司 用于传动带的横向段及用于无级变速器的传动带
EP3835618A1 (fr) * 2019-12-10 2021-06-16 Robert Bosch GmbH Segment transversal pour une courroie d'entraînement et courroie d'entraînement pour une transmission à variation continue comprenant le segment transversal et un empilement annulaire
NL1043501B1 (en) * 2019-12-10 2021-08-31 Bosch Gmbh Robert A transverse segment for a drive belt and a drive belt for a continuously variable transmission including the transverse segment and a ring stack
US11486464B2 (en) 2019-12-10 2022-11-01 Robert Bosch Gmbh Transverse segment for a drive belt and a drive belt for a continuously variable transmission including the transverse segment and a ring stack
CN112943862B (zh) * 2019-12-10 2025-09-02 罗伯特·博世有限公司 用于传动带的横向段及用于无级变速器的传动带

Also Published As

Publication number Publication date
CN110114591B (zh) 2021-11-26
NL1042198B1 (en) 2018-07-03
CN110114591A (zh) 2019-08-09
JP2020503484A (ja) 2020-01-30
KR20190104553A (ko) 2019-09-10
JP7009502B2 (ja) 2022-01-25

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